Roller-bearing



N. A. PALIVIGHEN.

l 19. LSQ lt, Patented NOVI 1159 WZL 10 SHEETS-SHEET l.

N VE N TU R I M Bj/ fior/1 2g/5,

"hwg:

N. A. PALIVIGREN.

ROLLER BEARING. 4 APPLICATION FILED ocT. I3, I9I

Patented Nov. 115, 192k. l0 SHEETS-SHEET 3.

W" im RRRRRRRRRRRR G.

EEEEEEEEEEEEEE 4.

INVENTOR I [ej @rma/om @We d burg:

NA A. PALMGREN.

ROLLER BEARING.

AhJcATloN FILED ocT.13,191

Patented Nov. 15, ILQZIL l0 SHEETS-SHEET 6.

N' MGREN.

R ARING. APPLICAT F' 0cT.13,191'9. 1,39%142., Patented Nov. 15, 19210 lo SHEETS-SHEET 7.

& INVENTOR I I I j' N. A. PALVIGREN. ROLLER BEARING. APFLxcATloN FILED ocr. 13. 1919.

Patnted Nov. )159 E921.,

1o' sHEETs-sHEET ro.

INVENTOR ULD Per

ornent mrs anun) ramaeninn, or eor'rnnrone, SWEDEN, assiduon vrc Axrrnnorfaen'r svnnsxa xurraennranmrn, or eorrrnnnona, swrnonn, a conronarron or SWEDEN'.

nonnen-emma.

arsenite.

Patented Nov. i5, 192i.;

Application led October 13, 1919. Serial NOSSOAOB.

To all rwiz/om t may concern:

Be it known that l NILs ARVID PALM- cREN, a subject of the ling of Sweden, re-

.for taking up radial pressure aswell as axial thrust, the latter in one direction or in both directions, the purpose of the invention being to provide a bearing in which the rollers are well guided. lin prior bearin s of the kind referred to the rollers are guided exclusively or mainly by the roller cage or retainer, but such guiding'is as a rule not very satisfactory.

ln contra-distinction hereto the bearing forming the subject of the present invention is -broadly characterized by the fact that each roller is'guided partly by at least one pressure Bange which prevents the roller from moving in direction toward its large end, and partly by at least one guide flange against which the roller bears in at least two points whichlie after one another in the direction of rolling so that the guide flange together with the pressure flange prevents displacement of the roller obliquely to the direction of rolling. ln this manner the rollers are guided exclusively or mainly by the race or races 'and not very considerably bythe roller retainer the purl pose of which is only to maintain the rollersV at definite distances from one another. The pressure iange may be formed in the well known manner and may bear against a portion of the rollerl also formed in therwellknown manner. On the other hand, the guide flange shouldpreferably be provided with a convex bear1ng surface if it is so placed in relation to the rollers that it suppressure only against the pressure flange, but merely.. Contact with the guide flange so that the bearing pressure against said flange is practically m'Z. Each roller will bear against the anges at least at three points, however, which points are so located as to form a triangle having a certain ex- .tension in the rolling direction, that is to say, in the tangential direction. Again, if a roller has a tendency to adjust itseli obliquely to the rolling direction it will also press against the guide iange in' such manner that two points on the end surfaces lof the roller Will bear with pressure against the fianges. @ne of said two points is located on the pressure flange andthe other point is located on the guide Harige, andthe two points have such positions relaf, tively to one another that the pressures at said points prevent a further oblique position of the roller.

' The pressure flanges and the guide flanges may be formed in the same yrace which arrangement provides the best guidingand is thus as a rule most suitable, butsaid flanges mayl also be formed on separate races. vlt is not necessary, however, that the flanges `be made integral with the race or races, but the may also be made as separate parts, in whlch case, however, they must be so located in the bearing as to be guided in the radial and axial directions, although they may be freely movable in tangential direction. l 1 A plurality of embodiments of the invention are shown by way of exampleiinf the.

one row project in between the rollers of the otherl row. Figs. 19 to 27 incl. show sections of different embodiments of single row radial pressure roller bearings which,

retainer.

vseparate ring which is guided in radial and axial directions, and Fig. 34 shows a tworow radial pressure bearing in which thel guide flange is made integral with the roller ferent axial thrust roller bearings, and finally/Figs. 37 to 65 incl. show further embodiments of the rollers.

vThe roller bearing illustrated in Fig. 1 is provided with an outer race 1 and an inner race 2, each of said races being made in one piece, and with two rows of conical rollers 3 which are inclined in opposite directions. In this manner the bearing becomes selfcontained, that is to say, it is held together by the rollers as a unit capable of being mounted, and it may take up not vonly radial pressure but. also axial thrust in both directions. Each` race is provided with two conical tracks or rolling surfaces for the rollers 3. For enabling/the rollers to be introduced into the bearing, it is provided with a filling opening 4. According to the present invention the inner race 2 is provided with two pressure flanges 5 and 6, one for each row of rollers, and with a guide flange '7 common to both rows of rollers, and which guide flange supports the rollers against inward movement. All of, said flanges are made integral with the inner race. Each roller is provided at its large end, which is directed outward from the center of the bearing, with a chamfer 8 which bears against the conical bearing surface 4on the pressure flange 5 or 6, so that the rollers are in this manner prevented from outwardrnovement, that is to say in the direction toward their large ends. ends of the rollers are spherically concave in such manner that the center of the sphere is located in the point or vertex of the cone, and the bearing surfaces of the guide flange 7 are spherically convex with the same radius and center, so that contact takes place between each roller and the bearing surface of the guide flange on a surface, that is to say, in a plurality ofpoints.

The distance between the pressure flange 5 or 6 and the guidel flange 7 is so adjusted that as long as each roller occupies its proper rolling position it bears with pressure only against the pressure flanges, contacting with the same by means of its chamfer 8 only in one point or along, a line, whereas it just Figs. 35 and 36 show two dif-,Y`

The end surfaces at the small' merely touches the guide flange, so that the bearing pressure on the bearing surface of -the guiding flange 7 .above referred'tois practically mZ. On account thereof the friction losses in the bearing surface also the roller tends to run ahead, or in the rear,`

of the small end. The pressure of the guide flange against the small end and the pressure of the' pressure flange against the large end,V which latter pressure always 'acts in a plane through the axes of the roller and of the bearing, form a -pair of forces which tend to turn the roller back into its proper position. The guide flangeand the pressure flange thus coact to prevent the rollers from adjusting themselves obliquelyfto the rolling direction.

" The thrust bearing illustrated in Fig. 2 is lprovided with a row of rollers 9 which have the same shape as the rollers in the radial pressure bearing described above and illustrated in Fig. 1. Each of the :races 10 and 11 is made in one piece, and the race 11 is provided with a pressure flange 12 and a guide flange 13, both of which are made integral with the race 11. The conical rollers bear with their large ends 'directed outwardv from the center of the bearing, against the pressure flange 12 and are thus prevented from outward movement, and their spherically concave end surfaces on the small ends contact with the convex bearing surface of the guide flange' 13, which surface forms a spherical zone the center of which coincides with the center of the bearing. The guiding of the rollers is thus also in thiscase effected by t-he two flanges in the Vsaine manner as above described. It will easily be understood that no filling opening is required in the bearing illustrated in Fig. 2.

In the single row radial pressure bearing illustrated i Fig. 3 the inner race 14 is provided with pressure flange 15 inthe middle and with two uide flanges 16 and 17 at the sides. The guide flan 16 supports the rollers 18 at their smal ends and is rovided with a convex bearing surface, w ile the flange 17 which supports the large ends of the rollers, has a concave bearing surface.

Each roller 18 is provided approximately l at its middle with a groove 19 one side surfacenof which forms a bearing surface. for the pressure flange 15.l The end surface at the small end of the roller is spherically con-;

memes the same as above described, with the diHerlence only, that the guiding becomes double in that, 1f a roller tends to adjust itself vobliquely, there will'be 'pressure at three places, 'namely one place on each Hange.

According to Fig. 4 the inner race 20 1s `provided with a Hange 21 which forms pressure Hange as well as guide Hange, and with a guide Hangew 22.- 'llhe Hrstnamed Hange supports the rollers 23 at the large ends, while the guide flange 22 which -is provided with a convex bearin "surface, contacts with the concave end sur aces at the small endsl the roller the pressure Hange 27 bears, so

' that also in this case it prevents the roller from moving in the direction toward its large end, to the right in' Fig.5. The guide Hange 28 supports the roller at the large end which is provided with a spherically con-- veX end surface.

The embodiment illustrated in Fig. 6 differs from the embodiment according ,t0 Fig. 5 only by the pressure Hange 32 and the guide Hange 33 being provided on the innerrace 34. The rollers 35 have the same shape as in Fig. 5, and the operation will thus also in this case be the same.

According to Fig. 7 the outer race 36 is provided with a pressure Hange 37 which supports the rollers 38 at the large ends, and with a guide Hange 39 having a spherically convex bearing surface which supports the rollers at the small ends.' The rollers are provided at the last mentioned ends with spherical'ly concave end surfaces. Again, according to Fig. 8 the inner race 40 is provided with a pressure Hange 41 which supports the rollers 42 -at the large ends, and witha guide Hange 43 which supports the rollersat the small ends where the rollers are provided with concave end surfaces. rlfhe bearing surface of the guide.

.assembled without filling opening, but each bearing can take up axial thrust only in one direction.

Figs. 9 to 17 incl. show a few diHerent shapes o f the end surfaces of the rollers whlch'are to'bear against the guide Hange. -Said flange is provided with al spherical bearing surface,.and the sphere is assumed to be continued in such manner that a s ection of the sphere ifn the plane of its great circle is obtained. 'llhe rollers are shown in axial sections. Fig. 9 illustrates the case corresponding to Figs. 5 and 6, that the end surface of the roller 44l and the bearing surface 45 of the guide Hange are spherical fand have the same radius. In Fig. 10 the end surface at the large end of the roller 46 portion 47 is plane. The roller will then bear only with the spherical zone of the end 'surface againstthe bearing surface 48 of the guide Hange. The roller 49 illustrated in Fig. 11 differs from the one shown in Fig-10 only by there being provided a central recess 50 in the end surface of the roller, the outer zone of the end surface still being spherical and bearing against the spherical bearing surface 51 of the guide Hange. According to Fig. 12 the end surface of the roller 52 `is plane, so that it only bears with its edges against thebearing surface 53 of the guide Hange. -lln such case, however, the

edges should preferably be slightly rounded v or chamfered so as to avoid that a/sharp edge on the roller bears under pressure against the guide Hange. For this purpose the ernbodiment illustrated in Fig. 13 may be chosen, for instance, according to which ernbodiment the roller 54 bears with its rounded edge 55 Vagainst the bearing surface' of the guide Hange.

On the other hand, if the guide Hange supports the roller at; its small end, the end surface of the ro er should be concave. Accordingly, as'Y shown `iu Fig. 14, the roller 57 -which bears against the convex bearing surface 59 of the guide'Hange. The radius of curvature o the end surface 58 is in this case smaller han that of the surface 59, so

that the Hrstnamed surface only bears with its edges against the lastmentioned surface.- On the other hand, according to Fig. 15, the end surface on the roller 60 and the bearing surface 61 of the guide Hange have the same radius of curvature, so that the wholeV of the Hrstnamed surface contacts with the lastmentioned surface.l Fig. 16 shows a similar construction, the only diHerence being that there is a central recess 63 in the end surface of the roller 62, so thatl only the outer zone of said end surface contactswith the .bearing surface 64 of the guide Hange. Finally, Fig. 17 illustrates the case that the v is provided with a concave end surface 58 end surface of the roller 65 is conical, the

conical surface contacting with the flange vsurface 66 on a circle.

lt will be understood from the examples Aabove described, that the surface of the rollers bearing against the guide ange should be concave if the flange supports the "rollers at their small ends, but convex if the flange supports the Vrollers at their large ends. ln any case said concave or convex surface 'onthe rollers should be a surface of vrotation the axis ofwhich coincides with the axis of the conical roller. 'The surface'of rotationmay' be a spherical Ccalotte, Figs.

9 and 15, or zone, Figs. 10, 11 and 16, having its center in the-point of the cone or located nearer to the roller than said point.

klit may also be a cone, 17 or a broken surface, that is to say, formed in such manner that only a certain zone of the end surface is formed as a sphere, a cone, or the like and the other portions as some other surface of rotation. If both `the end surface ofthe roller and the bearing surface of the lguide flange are spherical and have the same radius, surface contact will be obtained. lf

sure and guide flanges are provided on the inner race, in similar manner as in the embodiment illustrated in Fig. 1,' that is to say, the pressure flanges 68 support the rollers attheir large ends, and the guide flanges 69 provided with spherically convex bearing surfaces support the rollers at their small ends,

The construction of the single row radial pressure bearings above described and illustrated in Figs. 3 to 8 incl., is such that the bearings are not self-contained, and the races belongingto different bearings may therefore easily be`confounded, and one or more rollers may drop outl and become lost when the bearings are being mounted. In

.order to avoid this inconvenience it is suitable to provide the race which is not -pro- A vided with pressureand guide flanges, with a special retaining flange or locking flange which makes thel lbearing self-contained. For this purpose the locking flange should be provided-on the side of the bearing to-` ward whichthe large ends ofthe rollers are directed, and it may be provided with a filling opening for rendering it possible to Meana Aopening will be required. Furthermore, the

introduction of the full number of rollers may also be rendered possible by making the locking flange as a separate part, or by making the bearing with divided races, for

instance in such manner that eitherjthe guiding flange,- orthe pressure ilange',"i`or so possibly both. anges are Ina-de as separate parts. With the lastmentioned construction several advantages are attained' among which 'may be noted that the manufacture of the various parts, races and flanges, is materially facilitated, and that faults due to wear on the rollers or the races may be repaired by exchanging one or more small ring portions.

Figs. 19 to 27 incl. illustrate by way of example a few single row bearings which are provided with such locking flanges. lin the construction shown in Fig. 19 the inner race 70 is provided with a pressure ange 71 and a guide flange 72, the outer race 73 being provided with a\.loc king dange 74. Said last-mentionedvdange which is located at some distance from and outside of the large ends of the rollers 75, is made integral with the outer race, according to lthis construction. It will ybe understood from the drawing that said flange prevents the rollers from droppingout of the bearing, which will thus be self-contained. The inner race is divided, theV pressure flange 71 being made as a separate dpart and connected with the inner race proper by means of a sleeve 76 introduced into the inner race and ther pressure flange and bent outward at the ends. Fig. 20 shows a similar construction which differs from the one shown in Fig. 19 only by a slightly different shape of the separate part forming the pressure flange 77, which is provided with a cut 7 8 in the side directed toward the inner race 79. In this manner it' is attained that by exchanging the flange .77 it is possible tocompensate wear on the flanges and the-rollers. For such purpose,

according to Fig. 21, a loose ring 82 is in-4 serted between the ressure flange and the inner race 81. y inserting such rings of different thicknesses it is obviously possible to compensate the wear ron rollers and flanges.

Theembodiment shown in Fig. 22 differs from the construction illustrated in Fig. 19

only by the guide flange 83 of the inner race, instead of the pressure flange, being made as a separate part and connected with the inner race 84 by means of a sleeve 85'A bent outward at the ends. The outer race' 86 corresponds completely to that shown in Fig. 19, and like this flange it is provided with a locking flange 87 made integral with the outer race. Figs. 23 and 24 show` modilications of Fig. 22 similar to the modifications of Fig. 19 illustrated in Figs. 2O and 21, that is to say, according to Fig. 23 the guide flange 88 is provided with a cut 89, while according to Fig. 24 a loose ring 92 is provided between the guide flange 90 and the inner race 91, for the purpose of making it possible to compensate wear.

ln the construction illustrated in Fig. 25 the pressure flange 94 and the guide flange 95 are made integral with the inner race`93, whereas, on the other hand, the locking flange 97 on the outer race 96 is made as a separate part. The locking flange is rigidly connected with the outer race by means of a sleeve 98 provided around said ange and said race and bentl inward at the ends. According to Fig. 26 the locking flange 99 is also made as a separate part from the outer race 100, but it is made integral with a sleeve 101 placed around the outer race and riveted, so that in this manner the locking flange becomes rigidly connected with the outer race. Finally, Fig. 27 illustrates a construction in which both races are made integral with their flanges, the inner race 102 with the pressure flange 103, and the guide flange' 104 and the outer race 105 with the locking flange 106. For rendering it possible to introduce the rollers the locking flange is provided witha filling opening 107, and the opposing pressure flange on the inner race/.may simultaneously be provided with a similar opening 108. ln such case, however, said last-mentioned opening shouldV not extend all the way in to the conical, track on the inner race, but it should end at some distance above said track. 'lhe rollersinay then bev introduced either by forcing together the races, with or without heating the outer race, or possibly without forcing, provided that the outer race is moved in the direction toward the point of the rolling cones, which movement is possible if, as shown in Fig. 27, the locking flange does not touch the rollers in the normal position of the race but is at some distance from said rollers.

`Also in two-row bearings, in which no special locking ang'e is required for maintaining the bearing as a unit, it will often be advantageous to divide one of the races and, (for instance7 to make the pressure flanges or the guide flanges as separate parts. ln this manner it will be possible to avoid special lling openings, and the advantages in respect of manufacture andcompensation of wear above referred to are also attained. Figs. 28to 31 incl. show by way of example. a few two-row bearings with divided inner llts.

lboth rows 'of rollers and made integral with In the construction illustrated in Fig. 28 which most nearly resembles the bearing shown in F ig. 1, the inner race 109 is provided with a guide flange 110 common to the inner race, and with two pressure flanges 111 and 112 each of which is made as a separate part. Said pressure flanges are rigidly connected with the inner race by means of a sleeve 113 inserted through the inner race and through the two flanges and having its ends bent outward. According to Fig. 29 the two pressure Hanges 114 and 115 on the inner race is also'made as separate parts, but they are connected with the inner race 116 by means of screw threads. According to Fig. 30 the pressure flanges 117 and 118 are connected with the innerrace 119 by means of bolts 120 traversing the race and both flanges and riveted at the ends. Finally, Fig. 31 shows a construction in which the guide flange 121 is made as a separate part, the inner race being made in two portions 122 and 123 between which the guide flange is inserted. Fach of the two pressure anges 124 and 125 `is made integral with one of the portions of the inner race. The parts 121, 122 and 123 are held together by means of traversing bolts 126 riveted'at the ends.

ln all constructions above described the guide and ,pressure anges are either made integral with their races or, if they are made as separate parts, rigidly 4connected with the races: This last mentioned arrangement, 100 however,` is not necessary, but the anges, when made as separate parts, may also be so located in the bearing as to have a certain capacity of movement in the tangential div rection, vthat is to say, in the rolling direc- 105 tion, and thus are free to follow the rollers, whereas, on the other hand, they should be so guided in both radial and axial directions that they always occupy a definite position in these directions in relation to the 110 races.' lt may be advantageous to arrange particularly the guide flanges in this manner, an essentially facilitated manufcture of the races .being thus obtained as well as y less friction at the guide yflange which will 11.5

also be easily exchanged when worn.

Fig. 32 illustrates a two-row radial pressure bearing in which the guide flange common 4to both rows of rollers is made as a loose'l ring 127 located in the center of the 120 bearing. immediately inside of' the outer race 1.28. Said race is provided with two pressure flanges 129 and 130 which are made integral with the outer race and the last mentioned of which Hanges is provided with al25 filling opening. rlhe outward chamleredf large ends of the rollers bear against the pressure flanges, and the inner spherically concave end surfaces of the rollers bear against the ring 127 which is provided on at@ both sides with spherically convex bearing surfaces in the same manner as the stationary guide flange 7 in the bearing shown in Fig. 1. The ring 127 is prevented from'moving 'in axial direction by the rollers the movement of which is prevented by the pressure'flanges, and the ring is guided in radial direction by the rollers and the outer race against which the outer side of the ring bears. On the .other hand, the ring is freely movable in tangentialdirection, on account of which it willfollow the rollers at least to a certain degree when thev bearing is in operation, so that the friction between the rollers and the ring becomes decreased. YIt is also obvious that it is easier to manufacture the spherical bearing surfaces on the loose ring than on a flange integral with the race. The ring 127 in this construction is independent of the roller retainerf 131, which serves in the ordinary manner for maintaining the rollers at denite distances from one another.

The construction illustrated in Fig. 33 differs from the construction last described mainly by the two pressure flanges 132 and 133 being provided on the inner race 134, and by that, accordingly, the loose ring 135 forming the guide flange common to both rows of rollers, is located nearer to the inner race, although at some distance from Vthe same. The ring 135 is located inside of and is independent of the roller retainer 136 and is also in this case provided on both sides with spherically convex bearing surfaces against whichthe spherically concave end surfaces on the small ends ofthe rollers bear. The'ring is in this case guided in both c axial and radial directions by the rollers which in turn are guided by theV pressure flanges, but the ring is free to move in tangential direction.

Fig. 34 illustrates another modification of the bearing according to Fig. 32. The two pressure flanges 137 and 138 are also in this case provided on' and made integral with the outer race 139, but the ring 140- which forms the guide flange common to the two rows of rollers is in this case made integral with the roller retainer 141. The end surfaces at the small ends of the rollers are concave, and the bearing surfaces of the ring 140 are convex, but do not have spherical shape asa result of which'contact will take place between each roller and the guide ring 140 at two points. The ring is guided in radial and axial directions by the rollers, but it is free to move in the rolling direction, and the ring being' made integral with the roller. retainer it will of course move with the same speed as the rollers.

The arrangement of a guide flange freely movable in tangential direction is applicable also to axial thrust bearings. Fig. 35 illustrates an example of such an arrangement,

independent ofthe roller retainer 146, which may be made for `instance ofl pressed sheet v v so 1 metal. Y "F ig. 36 shows a modification of ,the axial thrustbearing illustrated in Fig. 2 which .l differs from said bearing only as regards 1 the shape of the bearing surface of the guidey flange. The pressure flange 147 as well as the guide flange 148 are made integralwith the one race 149, but the bearing surface o f the guide flange against whichfsurface the f small ends of the rollers 150 bear, is not Spherical, on account of which therewill be contact between each roller and: the guide flange at two points in the same manner as in the construction shown in Fig..34.

The constructions above described and illustrated in the drawings may, of course, 'be further modified in several respects with- -out departing from the principle of the 1n` vention. -Thus it is, for instance, not necessary that the rollers bear directly aga1nst the guide flange, but they may also bear against special loose members which in turn bear against the ide flange or flanges. Furthermore, the s Vape of the rollers may also be varied in several respects, as will be evident from Figs. 37 to 65 incl. which show some useful shapes of the rollers. In

all these figures, the surfaces on the rollers Y whichare to bear against pressure flanges, are indicated at T, while the surfaces which are to bear against guide flanges, are indicated at S. In order to attain an eflcient guiding it is advantageous that the pressure and guide flanges, and thus also the ycorrespending surfaces on the rollers, are located adjacent one another, as shown for instance in Figs. 39 and 40. The portions of the rollers which are to bear against the pressure or guide flanges, may consist `,of wash ers or the like which are pivoted on the roller proper, as shown for instance in Figs. 49 and 51. The rollers may also be bored and may rotate on studs in the roller retainer and, finally, each roller may be composed of several parts, as shown for instance in Figs. 63 to 65 incl. The rollers may be located in the bearing in such manner that the points ofthe cones lie on the geometrical axis of the bearing, but the points may also lie to the one or the other side of said axis in order that the rollers shall more easily maintain their proper. positions in the bearing.

li claim:

l, lin a roller bearing, the combination of an inner race, an outerrace, conical rollers, at least one pressure Harige preventing the rollers from moving in direction toward their large ends, and atleast one guide Harige against which each roller bears in at least two points which lie after one another in the rolling direction so that'said guide Harige together with said pressure flange prevents the roller from disp-lacing itself obliquely, to the rolling direction.

2.. linl a roller bearing, the combination of an innerrace, an outer race, conical rollers, at least one pressure Harige preventing the rollers from moving in direction toward their large ends, and at least'one guide Harige having a convex bearing surface against which each roller bears in at least two points which lie after one another in the rolling direction, said guide flange being so located as to prevent the rollers from moving iii direc-- tion toward their small ends.

i v3, ln a roller bearing, the combination of an inner race, an outer race, conical rollers, at least one pressure Harige preventing the rollers from moving in direction toward their large ends, and atleast one guide flange having a convex bearing surface against which each roller bears in at least two points which lie after one another in the rolling direction, the end surfaces on the rollers bearing against said guide flange being concave.

4: ln a roller bearing, the combination of an inner race, an outer race, conical rollers, at least one pressure Harige preventing the rollers from moving in direction toward their large ends, and at least one guide Hange against which each roller bears in at least two points which lie after one another in the rolling direction so that said guide flange together with said pressure flange prevents the roller from displacing itself obliquely to the rolling direction, said pressure Hange and said guide flange being provided on one and the same race.

5. vln a roller bearing, the combination of an inner race, an outer race, conical rollers, at least one pressure Harige preventing the rollers from moving in direction toward their large ends, and at least one guide flange against which each roller bea-rs in at least twopoints which lie after one another iii the rolling direction so that said guide flange together with said pressure flange prevents the roller from displacing itself obliquely to the rolling direction, said pressure flange and said guide Harige being made integral with one of the races.

6. lin a roller bearing, the combination of an inner race, an outer race, conical rollers,

,the roller from displacing itself obliquely to the rolling direction, each of said pressure and guide flanges being made integral with one of said races.

7. lin a roller bearing, the combination of an inner race, an outer race, conical rollers,

at least one pressure Harige preventing the.

rollers from moving in direction 'toward their large ends, and at leastone guide flange having a convex bearing surface against which each roller bears in at least two points which lie after one another in the rolling direction, the end surfaces on the rollers bearing against said guide Harige being spherically concave in such manner that the center of the sphere lies in the point of the cone, and they bearing surface of the guide flange being spherically convex having the saine radius and center, so -that there will be surface con.- tact between each roller and the bearing surface of said guide flange.

8. ln a roller bearing, the combination of a pair of opposed races, rollers between said races, and a flange on one of said races arranged to contact with said rollers, the contacting surface on said flange being spherical and the coperating` surface oneach roller being correspondingly spherical so that there is contact between said surfaces over a surface.

9. ln a roller bearing, the combination of an inner race, an outer race, rollers therebetween, and a Harige on one of said races arranged to contact with said rollers, the contacting surface on said flange being spherical and the cooperating surface on each roller being correspondingly spherical so that there is contact between said surfaces over a surface.

10. lin a roller bearing, the combination of an inner race, an outer race,ftwo series of lrollers therebetween, and a Harige on one of said races arranged between the two series off rollers and provided with surfaces against which the ends of the rollers of the two series contact, the contacting surfaces on said Harige being vspherical andthe co# operating surface on each roller being correspondingly spherical so that there is contact between said surfaces over a surface.

11. A roller bearing according to claim 8 characterized by the fact that the Harige therein recited is a guiding Hange as distinguished from a pressure Harige.,

12. A roller bearing according to claini 9 characterized by the fact that one of the races is provided with a further Harige bear'- ing against and preventing the said rollers from moving in their axial direction.

13. In a roller bearing, the combination of a pair of opposed races, rollers therebetween, a guiding flange on one of said races arranged to contact with said rollers, the contactin surface on said flange being spherical and t e coperating surface on each roller being correspondingly spherical, and a pres cited is generated from a point located in the axis of rotation ofthe bearing as a center.v

15. In a roller bearing the combination of a pair of opposed races, rollers therebetween and a guiding iange on one'of said .races arranged to Contact with said rollers, the

contacting surface on said flange being spherical and generated from a point located in the .axis of rotation of the bearing as a center, and the coperating surface on each roller being correspondingly spherical so that there is contact between said sur- :faces over a surface.

1 NiLs ARVID PALMGREN. 

